U.S. patent number 10,281,007 [Application Number 15/473,658] was granted by the patent office on 2019-05-07 for speed reducer.
This patent grant is currently assigned to NIDEC SHIMPO CORPORATION. The grantee listed for this patent is Nidec Shimpo Corporation. Invention is credited to Yuji Maeguchi, Kenji Sugishita, Taihei Tsubone.
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United States Patent |
10,281,007 |
Sugishita , et al. |
May 7, 2019 |
Speed reducer
Abstract
A speed reducer includes an input shaft member including a sun
rotor arranged to rotate about a central axis; one or more
planetary rolling elements each of which is supported to be capable
of rotating around the sun rotor; a tubular eccentric shaft
including an outer circumferential surface eccentric with respect
to the central axis, and arranged to rotate about the central axis
along with the rotation of the one or more planetary rolling
elements; an eccentric oscillating gear including a plurality of
external teeth in an outer circumferential surface thereof, and
supported by the eccentric shaft through a first bearing; a housing
including internal teeth arranged to mesh with the external teeth
of the eccentric oscillating gear in an inner circumferential
surface thereof; an output flange arranged to rotate about the
central axis together with the eccentric oscillating gear, and
including an eccentric oscillating carrier pin arranged to pass
through the eccentric oscillating gear in an axial direction; and
one or more second bearings arranged radially between an inner
circumferential surface of the eccentric shaft and the input shaft
member.
Inventors: |
Sugishita; Kenji (Nagaokakyo,
JP), Tsubone; Taihei (Nagaokakyo, JP),
Maeguchi; Yuji (Nagaokakyo, JP) |
Applicant: |
Name |
City |
State |
Country |
Type |
Nidec Shimpo Corporation |
Nagaokakyo-shi, Kyoto |
N/A |
JP |
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Assignee: |
NIDEC SHIMPO CORPORATION
(Kyoto, JP)
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Family
ID: |
59566337 |
Appl.
No.: |
15/473,658 |
Filed: |
March 30, 2017 |
Prior Publication Data
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Document
Identifier |
Publication Date |
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US 20170314644 A1 |
Nov 2, 2017 |
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Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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62291233 |
Feb 4, 2016 |
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Foreign Application Priority Data
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Jun 21, 2016 [JP] |
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2016-122963 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16H
1/32 (20130101); F16H 2001/325 (20130101); F16H
2001/327 (20130101) |
Current International
Class: |
F16H
1/32 (20060101) |
Field of
Search: |
;475/162,168,169,178,179 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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2007-078010 |
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Mar 2007 |
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JP |
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2009-127700 |
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Jun 2009 |
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JP |
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Primary Examiner: Nicholson, III; Leslie A
Attorney, Agent or Firm: Keating & Bennett, LLP
Parent Case Text
CROSS REFERENCE TO RELATED APPLICATIONS
This application claims the benefit of priority to U.S. Patent
Application No. 62/291,233 filed on Feb. 4, 2016 and claims the
benefit of priority to Japanese Patent Application No. 2016-122963
filed on Jun. 21, 2016. The entire contents of each of these
applications are hereby incorporated herein by reference.
Claims
What is claimed is:
1. A speed reducer comprising: an input shaft member including a
sun rotor arranged to rotate about a central axis; one or more
planetary rolling elements each of which is supported to be capable
of rotating around the sun rotor; a tubular eccentric shaft
including an outer circumferential surface eccentric with respect
to the central axis, and arranged to rotate about the central axis
along with the rotation of the one or more planetary rolling
elements; an eccentric oscillating gear including a plurality of
external teeth in an outer circumferential surface thereof, and
supported by the eccentric shaft through a first bearing; a housing
including internal teeth arranged to mesh with the external teeth
of the eccentric oscillating gear in an inner circumferential
surface thereof; an output flange arranged to rotate about the
central axis together with the eccentric oscillating gear, and
including an eccentric oscillating carrier pin arranged to pass
through the eccentric oscillating gear in an axial direction; one
or more second bearings arranged radially between an inner
circumferential surface of the eccentric shaft and the input shaft
member; and one or more third bearings arranged radially between
the eccentric shaft and the output flange.
2. The speed reducer according to claim 1, wherein each of the one
or more planetary rolling elements is arranged to rotate by
receiving power from the sun rotor while being in contact with both
the sun rotor and the eccentric shaft.
3. The speed reducer according to claim 1, wherein at least one of
the one or more second bearings is arranged to axially overlap with
at least one of the one or more third bearings.
4. The speed reducer according to claim 1, wherein each of the one
or more planetary rolling elements is a helical gear; and at least
one of the one or more second bearings is a ball bearing.
5. The speed reducer according to claim 1, wherein at least one of
the one or more second bearings is a needle bearing.
6. The speed reducer according to claim 1, wherein the one or more
planetary rolling elements are arranged to radially overlap with
the eccentric shaft.
7. The speed reducer according to claim 1, wherein at least one of
the one or more second bearings is arranged to radially overlap
with the eccentric outer circumferential surface of the eccentric
shaft.
8. The speed reducer according to claim 1, further comprising: a
carrier including a carrier pin or pins arranged to support the one
or more planetary rolling elements; and an internal ring in a shape
of a circular ring, including a contact surface arranged to make
contact with the one or more planetary rolling elements, and
arranged radially outward of the one or more planetary rolling
elements; wherein the eccentric shaft is arranged to receive power
from the one or more planetary rolling elements through the
internal ring; the carrier is fixed to the output flange; and the
input shaft member and the eccentric shaft are arranged to rotate
about the central axis in opposite directions.
9. The speed reducer according to claim 1, further comprising: a
carrier including a carrier pin or pins arranged to support the one
or more planetary rolling elements; and an internal ring in a shape
of a circular ring, including a contact surface arranged to make
contact with the one or more planetary rolling elements, and
arranged radially outward of the one or more planetary rolling
elements; wherein the carrier is fixed to the eccentric shaft; the
eccentric shaft is arranged to receive power through the carrier;
and the input shaft member and the eccentric shaft are arranged to
rotate about the central axis in a same direction.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a speed reducer.
2. Description of the Related Art
A combination speed reducer that achieves a speed reduction with a
high reduction ratio in multiple steps using a combination of a
planetary gear speed reduction mechanism and an eccentrically
oscillating speed reducer has been known. Such a known combination
speed reducer is described in, for example, JP-A 2007-78010.
However, the combination speed reducer described in JP-A 2007-78010
has a complicated structure, with the planetary gear speed
reduction mechanism and the eccentrically oscillating speed reducer
being arranged at positions away from each other, and it is
difficult to reduce the size of the combination speed reducer.
Moreover, no bearing is arranged between a sun gear of the
planetary gear speed reduction mechanism and a crankshaft of the
eccentrically oscillating speed reducer, and it is difficult to
cause centers of rotation thereof to coincide with each other. This
may lead to a deterioration in rotational accuracy and an increase
in wear.
SUMMARY OF THE INVENTION
A speed reducer according to a preferred embodiment of the present
invention includes an input shaft member including a sun rotor
arranged to rotate about a central axis; one or more planetary
rolling elements each of which is supported to be capable of
rotating around the sun rotor; a tubular eccentric shaft including
an outer circumferential surface eccentric with respect to the
central axis, and arranged to rotate about the central axis along
with the rotation of the one or more planetary rolling elements; an
eccentric oscillating gear including a plurality of external teeth
in an outer circumferential surface thereof, and supported by the
eccentric shaft through a first bearing; a housing including
internal teeth arranged to mesh with the external teeth of the
eccentric oscillating gear in an inner circumferential surface
thereof; an output flange arranged to rotate about the central axis
together with the eccentric oscillating gear, and including an
eccentric oscillating carrier pin arranged to pass through the
eccentric oscillating gear in an axial direction; and one or more
second bearings arranged radially between an inner circumferential
surface of the eccentric shaft and the input shaft member.
In the above preferred embodiment of the present invention, a
bearing is arranged between the sun rotor of a planetary gear speed
reduction mechanism and the eccentric shaft of an eccentrically
oscillating speed reducer to increase precision with which members
of the speed reducer are arranged. This contributes to reducing
wear and damage of the members of the speed reducer.
The above and other elements, features, steps, characteristics and
advantages of the present invention will become more apparent from
the following detailed description of the preferred embodiments
with reference to the attached drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a vertical sectional view of a speed reducer according to
a preferred embodiment of the present invention.
FIG. 2 is a horizontal sectional view of the speed reducer
according to a preferred embodiment of the present invention.
FIG. 3 is a horizontal sectional view of the speed reducer
according to a preferred embodiment of the present invention.
FIG. 4 is a vertical sectional view of a speed reducer according to
another preferred embodiment of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Hereinafter, preferred embodiments of the present invention will be
described with reference to the accompanying drawings. It is
assumed herein that a direction parallel to a central axis of an
input shaft member or a sun rotor is referred to by the term "axial
direction", "axial", or "axially", that directions perpendicular to
the central axis are each referred to by the term "radial
direction", "radial", or "radially", and that a direction along a
circular arc centered on the central axis is referred to by the
term "circumferential direction", "circumferential", or
"circumferentially". Note, however, that the term "parallel" as
used above includes both "parallel" and "substantially parallel".
Also note that the term "perpendicular" as used above includes both
"perpendicular" and "substantially perpendicular". In the following
description, the right side and the left side in FIGS. 1 and 4 will
be referred to as an "input side" and an "output side",
respectively, for the sake of convenience in description.
FIG. 1 is a vertical sectional view of a speed reducer 1A according
to a first preferred embodiment of the present invention taken
along a plane including a central axis 90A. FIG. 2 is a horizontal
sectional view of the speed reducer 1A taken along line A-A in FIG.
1. FIG. 3 is a horizontal sectional view of the speed reducer 1A
taken along line B-B in FIG. 1.
The speed reducer 1A is an apparatus that converts rotational
motion at a first rotation rate obtained from an external electric
motor (not shown) or the like to rotational motion at a rotation
rate lower than the first rotation rate in two steps, and causes an
output flange 30A to rotate at the rotation rate lower than the
first rotation rate. The speed reducer 1A is, for example,
installed in a joint portion of an arm of a work robot to realize
bending and stretching of the arm. Note that electric
motor-attached speed reducers including speed reducers according to
preferred embodiments of the present invention may be installed in
other devices, such as, for example, a powered exoskeleton, a
turntable, an index plate of a machine tool, a wheelchair, and an
automated guided vehicle, to realize various types of rotational
motion.
As illustrated in FIG. 1, the speed reducer 1A according to the
present preferred embodiment includes an input shaft member 10A, a
speed reduction mechanism 20A, and the output flange 30A.
The input shaft member 10A is a member that rotates at the first
rotation rate, which is a rotation rate inputted from an outside.
The input shaft member 10A according to the present preferred
embodiment includes an input shaft 13A and a sun rotor 14A. The
input shaft 13A is a cylindrical member arranged to extend along
the central axis 90A. An input-side end portion 131A of the input
shaft 13A is connected to a motor that serves as a driving source
directly or through another power transmission mechanism. Once the
motor is driven, the input shaft member 10A is caused to rotate
about the central axis 90A at the first rotation rate.
The sun rotor 14A is arranged to rotate about the central axis 90A
together with the input shaft 13A. The sun rotor 14A includes a
plurality of sun teeth 141A arranged to project radially
outward.
The speed reduction mechanism 20A is a mechanism arranged between
the input shaft member 10A and the output flange 30A to transfer
the rotational motion of the input shaft member 10A to the output
flange 30A while reducing the speed thereof in two steps. The speed
reduction mechanism 20A according to the present preferred
embodiment includes a plurality of planetary rolling elements 26A,
an eccentric shaft 21A, eccentric oscillating gears (a first
eccentric oscillating gear 22A and a second eccentric oscillating
gear 82A), and a housing 23A.
The planetary rolling elements 26A are arranged at regular
intervals around the sun rotor 14A. Each planetary rolling element
26A includes an insert hole 260A in a center thereof. A planetary
carrier pin 33A is inserted in the insert hole 260A. Each planetary
rolling element 26A is supported by the planetary carrier pin 33A
to be capable of rotating and revolving around the sun rotor 14A.
The planetary carrier pins 33A are included in a planetary carrier
34A disposed on the output side. Further, the planetary carrier 34A
is fixed to the output flange 30A, which will be described below,
through bolts or the like. In addition, an outer circumferential
portion of each planetary rolling element 26A includes a plurality
of planetary teeth 261A arranged to mesh with the sun teeth 141A of
the sun rotor 14A. Accordingly, rotation of the sun rotor 14A
causes each planetary rolling element 26A to rotate in a direction
opposite to a direction in which the input shaft member 10A and the
sun rotor 14A rotate. Note that, although the speed reducer 1A
according to the present preferred embodiment includes four
planetary rolling elements 26A as illustrated in FIG. 2, the number
of planetary rolling elements 26A may alternatively be one, two,
three, or more than four. Also note that the planetary rolling
elements 26A may alternatively be arranged at irregular intervals
around the sun rotor 14A.
The eccentric shaft 21A is a tubular member arranged radially
outward of the planetary rolling elements 26A, and including an
outer circumferential surface which is eccentric with respect to
the central axis 90A. An inner circumferential portion of the
eccentric shaft 21A defines an internal ring in the shape of a
circular ring, including a contact surface arranged to make contact
with the planetary rolling elements 26A, and including a plurality
of internal teeth 212A arranged to mesh with the planetary teeth
261A. That is, the planetary teeth 261A of each of the planetary
rolling elements 26A constantly mesh with both the sun teeth 141A
of the sun rotor 14A and the internal teeth 212A of the eccentric
shaft 21A. The eccentric shaft 21A receives power from the
planetary rolling elements 26A through the internal ring including
the internal teeth 212A. As described above, once the sun rotor 14A
rotates, each of the planetary rolling elements 26A rotates about
the planetary carrier pin 33A. Accordingly, the eccentric shaft 21A
slowly rotates about the central axis 90A at a second rotation rate
lower than the first rotation rate of the input shaft member 10A
and the sun rotor 14A in the direction opposite to the direction in
which the input shaft member 10A and the sun rotor 14A rotate.
Note that "helical gears", for example, are used as the sun rotor
14A, the planetary rolling elements 26A, and the internal ring of
the eccentric shaft 21A. Note, however, that members having
structures other than those of the "helical gears", such as, for
example, "spur gears" or "traction rollers", may alternatively be
used as the sun rotor 14A, the planetary rolling elements 26A, and
the internal ring of the eccentric shaft 21A.
The first eccentric oscillating gear 22A is attached to an
eccentric outer circumferential surface 211A of the eccentric shaft
21A through a first bearing 24A. Therefore, the first eccentric
oscillating gear 22A is supported to be rotatable about a first
central axis 91A, which is a center of the eccentric outer
circumferential surface 211A of the eccentric shaft 21A. Similarly,
the second eccentric oscillating gear 82A is attached to an
eccentric outer circumferential surface 811A of the eccentric shaft
21A through a first bearing 84A. Therefore, the second eccentric
oscillating gear 82A is supported to be rotatable about a second
central axis 92A, which is a center of the eccentric outer
circumferential surface 811A of the eccentric shaft 21A. Note that,
although the speed reducer 1A illustrated in FIG. 1 includes two
eccentric oscillating gears, the number of eccentric oscillating
gears is not limited to two.
As illustrated in an enlarged view in FIG. 3, the first eccentric
oscillating gear 22A includes a plurality of external teeth 41A
arranged to project radially outward in an outer circumferential
surface thereof. In addition, an external tooth space 42A, which is
recessed radially inward, is defined between adjacent ones of the
external teeth 41A. The external teeth 41A and the external tooth
spaces 42A are arranged alternately in a circumferential direction
about the first central axis 91A. In addition, similarly to the
first eccentric oscillating gear 22A, the second eccentric
oscillating gear 82A includes a plurality of external teeth (not
shown) and a plurality of external tooth spaces (not shown) in an
outer circumferential portion thereof.
In addition, the first eccentric oscillating gear 22A includes a
plurality of insert holes 43A. The insert holes 43A are arranged at
regular intervals in the circumferential direction about the first
central axis 91A. Each insert hole 43A is arranged to pass through
the first eccentric oscillating gear 22A in an axial direction,
radially inside of the external teeth 41A and the external tooth
spaces 42A. Note that, although the speed reducer 1A illustrated in
FIG. 3 includes eight insert holes 43A, the number of insert holes
43A is not limited to eight. Similarly to the first eccentric
oscillating gear 22A, the second eccentric oscillating gear 82A
also includes a plurality of insert holes 43A.
The housing 23A is a substantially cylindrical member arranged to
house the input shaft member 10A, the planetary rolling elements
26A, the eccentric shaft 21A, the eccentric oscillating gears
(i.e., the first eccentric oscillating gear 22A and the second
eccentric oscillating gear 82A), and the output flange 30A therein.
As illustrated in the enlarged view in FIG. 3, the housing 23A
includes a plurality of internal teeth 51A arranged to project
radially inward in an inner circumferential surface thereof. In
addition, an internal tooth space 52A, which is recessed radially
outward, is defined between adjacent ones of the internal teeth
51A. The internal teeth 51A and the internal tooth spaces 52A are
arranged alternately in a circumferential direction about the
central axis 90A.
The external teeth 41A of the first eccentric oscillating gear 22A
and the internal teeth 51A of the housing 23A are arranged to mesh
with each other. That is, when the speed reducer 1A is in
operation, the first eccentric oscillating gear 22A rotates while
the external teeth 41A of the first eccentric oscillating gear 22A
are fitted in the internal tooth spaces 52A of the housing 23A, and
the internal teeth 51A of the housing 23A are fitted in the
external tooth spaces 42A of the first eccentric oscillating gear
22A. Similarly, the external teeth (not shown) of the second
eccentric oscillating gear 82A and the internal teeth 51A of the
housing 23A are arranged to mesh with each other. In the present
preferred embodiment, the housing 23A thus serves as an internal
gear. Note that an internal gear separate from the housing 23A may
alternatively be arranged on an inner circumferential portion of
the housing 23A.
Each of the first and second eccentric oscillating gears 22A and
82A rotates by meshing with the internal teeth 51A of the housing
23A while revolving around the central axis 90A through the
planetary rolling elements 26A and the eccentric shaft 21A due to
power from the input shaft member 10A. Here, the number of internal
teeth 51A of the housing 23A is greater than the number of external
teeth 41A of the first eccentric oscillating gear 22A. Therefore,
with each revolution of the first eccentric oscillating gear 22A,
the position of the external tooth 41A that meshes with the same
internal tooth 51A of the housing 23A shifts. Thus, the first
eccentric oscillating gear 22A slowly rotates at a third rotation
rate lower than the second rotation rate in a direction opposite to
a direction in which the eccentric shaft 21A rotates, that is, in
the same direction as the rotation direction of the input shaft
member 10A and the sun rotor 14A. Accordingly, the position of each
insert hole 43A of the first eccentric oscillating gear 22A also
slowly rotates at the third rotation rate. Similarly, the second
eccentric oscillating gear 82A slowly rotates at the third rotation
rate lower than the second rotation rate in the direction opposite
to the direction in which the eccentric shaft 21A rotates, that is,
in the same direction as the rotation direction of the input shaft
member 10A and the sun rotor 14A.
If the number of external teeth 41A of the first eccentric
oscillating gear 22A is denoted by N, and the number of internal
teeth 51A of the housing 23A is denoted by M, a reduction ratio P
is given by P=(second rotation rate)/(third rotation rate)=N/(M-N).
In the example of FIG. 3, N=59 and M=60, and therefore, the
reduction ratio in this example is P=59. That is, the third
rotation rate is equal to 1/59 times the second rotation rate. Note
that the reduction ratio of a speed reduction mechanism according
to another preferred embodiment of the present invention may have
another value. The number of external teeth (not shown) of the
second eccentric oscillating gear 82A is equal to the number of
external teeth 41A of the first eccentric oscillating gear 22A.
As illustrated in FIGS. 1 and 3, a plurality of second bearings 25A
are further arranged radially between an inner circumferential
surface of the eccentric shaft 21A and the input shaft member 10A.
This contributes to increasing precision with which each member of
the speed reducer 1A is arranged. This in turn contributes to
stabilizing rotation of the eccentric shaft 21A and each eccentric
oscillating gear, and reducing wear and damage of each member, and
also contributes to extending the life of the speed reducer 1A.
Note that, although the speed reducer 1A illustrated in FIG. 1
includes two second bearings 25A, the number of second bearings 25A
may alternatively be one or more than two.
At least one of the plurality of second bearings 25A (a second
bearing 25A1 in FIG. 1) is preferably a ball bearing. In the case
where the "helical gear" is used as each of the planetary rolling
elements 26A as described above, an axial load occurs. In this
case, use of the ball bearing leads to easier absorption of the
axial load. In addition, at least one of the second bearings 25A (a
second bearing 25A2 in FIG. 1) is preferably a needle bearing. This
contributes to reducing the radial dimension of the speed reducer
1A.
Further, as illustrated in FIG. 1, at least one of the plurality of
second bearings 25A of the speed reducer 1A is arranged to radially
overlap with the eccentric outer circumferential surface 211A of
the eccentric shaft 21A. This contributes to reducing the axial and
radial dimensions of the speed reducer 1A.
The output flange 30A includes a first disk 31A, a second disk 32A,
and a plurality of eccentric oscillating carrier pins 44A arranged
to pass through the eccentric oscillating gears (i.e., the first
and second eccentric oscillating gears 22A and 82A) in the axial
direction.
The first disk 31A is a member in the shape of a circular ring and
arranged to be perpendicular to the central axis 90A. The first
disk 31A is arranged on the output side of the first and second
eccentric oscillating gears 22A and 82A.
A third bearing 60A is further arranged radially between the
eccentric shaft 21A and the first disk 31A of the output flange
30A. This contributes to further increasing the precision with
which the output flange 30A is arranged in the speed reducer 1A.
This in turn contributes to stabilizing rotation of the output
flange 30A, and further reducing the wear and damage of each
member, and also contributes to further extending the life of the
speed reducer 1A.
In addition, the first disk 31A includes a plurality of (eight in
the present preferred embodiment) press-fit holes 311A in which the
eccentric oscillating carrier pins 44A are press fitted. The
press-fit holes 311A are arranged at regular intervals in the
circumferential direction about the central axis 90A. Each
press-fit hole 311A is arranged to pass through the first disk 31A
in the axial direction.
The second disk 32A is a member in the shape of a circular ring and
arranged to be perpendicular to the central axis 90A. The second
disk 32A is arranged on the input side of the first and second
eccentric oscillating gears 22A and 82A.
A third bearing 60A is arranged radially between the eccentric
shaft 21A and the second disk 32A of the output flange 30A. This
contributes to further increasing the precision with which the
output flange 30A is arranged in the speed reducer 1A. This in turn
contributes to stabilizing the rotation of the output flange 30A,
and further reducing the wear and damage of each member, and also
contributes to further extending the life of the speed reducer 1A.
Note that, although the speed reducer 1A illustrated in FIG. 1
includes two third bearings 60A, the number of third bearings 60A
may alternatively be one or more than two.
In addition, the second disk 32A includes a plurality of (eight in
the present preferred embodiment) fixing holes 321A in which
input-side end portions of the eccentric oscillating carrier pins
44A are inserted. The fixing holes 321A are arranged at regular
intervals in the circumferential direction about the central axis
90A. Each fixing hole 321A is arranged to pass through the second
disk 32A in the axial direction.
Each of the plurality of (eight in the present preferred
embodiment) eccentric oscillating carrier pins 44A is a columnar
member arranged to connect the first and second disks 31A and 32A
to each other. Each eccentric oscillating carrier pin 44A is
arranged to be parallel or substantially parallel to the central
axis 90A. The eccentric oscillating carrier pins 44A are press
fitted in the respective press-fit holes 311A of the first disk
31A, and are inserted through the respective insert holes 43A of
each of the first and second eccentric oscillating gears 22A and
82A. In addition, a coming-off preventing portion 331A having an
increased diameter is arranged at an output-side end portion of
each eccentric oscillating carrier pin 44A. The coming-off
preventing portion 331A is arranged to be in axial contact with the
first disk 31A. Each eccentric oscillating carrier pin 44A is thus
prevented from coming off to the input side. In addition, the
input-side end portion of each eccentric oscillating carrier pin
44A is inserted in the corresponding fixing hole 321A of the second
disk 32A, and is fixed to the second disk 32A through a nut or the
like.
As illustrated in FIG. 3, there is a gap between a surface defining
each insert hole 43A and an outer circumferential surface of the
eccentric oscillating carrier pin 44A. A bushing ring 61A in the
shape of a circular ring is inserted in this gap. Once each of the
first and second eccentric oscillating gears 22A and 82A rotates at
the third rotation rate, which results from a speed reduction,
power of the rotation is transferred to each eccentric oscillating
carrier pin 44A through the bushing ring 61A. As a result, the
eccentric oscillating carrier pins 44A and the output flange 30A,
which includes the eccentric oscillating carrier pins 44A, rotate
about the central axis 90A at the third rotation rate together with
the two eccentric oscillating gears.
Further, the planetary carrier 34A, which is fixed to the output
flange 30A, and the planetary carrier pins 33A, which are included
in the planetary carrier 34A, rotate about the central axis 90A
along with the rotation of the output flange 30A. Accordingly, the
planetary rolling elements 26A, which are supported by the
planetary carrier pins 33A, revolve around the central axis 90A.
That is, the planetary rolling elements 26A revolve around the
central axis 90A while rotating by receiving power through the sun
rotor 14A or the planetary carrier pins 33A while being in contact
with both the sun rotor 14A and the eccentric shaft 21A.
As described above, the eccentric shaft 21A of the speed reducer 1A
according to the present preferred embodiment slowly rotates in the
direction opposite to the direction in which the input shaft member
10A and the sun rotor 14A rotate through the planetary rolling
elements 26A due to power by the input shaft member 10A including
the sun rotor 14A. Each planetary rolling element 26A of the speed
reducer 1A is arranged to radially overlap with the eccentric shaft
21A including the internal ring. This contributes to reducing the
axial dimension of the speed reducer 1A.
Next, a second preferred embodiment of the present invention will
now be described below. FIG. 4 is a vertical sectional view of a
speed reducer 1B according to the second preferred embodiment of
the present invention taken along a plane including a central axis
90B. Note that the second preferred embodiment will be described
below with focus on differences from the first preferred
embodiment, and that features of the second preferred embodiment
which are shared by the first preferred embodiment will not be
described to avoid redundancy.
As illustrated in FIG. 4, a portion of the speed reducer 1B
according to the second preferred embodiment in the vicinity of the
central axis 90B projects to the output side. More specifically, a
sun rotor 14B, a plurality of planetary rolling elements 26B, and
an internal ring 36B are arranged to project to the output side
relative to a first disk 31B of an output flange 30B. The speed
reducer 1B having the above structure is also able to achieve
reductions in the axial dimensions of the speed reducer 1B and a
device as a whole to which the speed reducer 1B is attached, when
the internal ring 36B, which is arranged radially outward of the
planetary rolling elements 26B, is buried in the device.
Similarly to the speed reducer 1A according to the first preferred
embodiment, the speed reducer 1B according to the present preferred
embodiment includes an input shaft member 10B, a speed reduction
mechanism 20B, and the output flange 30B. Once a motor is driven,
the input shaft member 10B, which includes the sun rotor 14B,
rotates about the central axis 90B at a first rotation rate, which
is a rotation rate inputted from an outside. The speed reduction
mechanism 20B includes the planetary rolling elements 26B, an
eccentric shaft 21B, a plurality of eccentric oscillating gears (a
first eccentric oscillating gear 22B and a second eccentric
oscillating gear 82B), the internal ring 36B, and a housing
23B.
The planetary rolling elements 26B are arranged at regular
intervals around the sun rotor 14B. Each planetary rolling element
26B includes an insert hole 260B in a center thereof. A planetary
carrier pin 33B is inserted in the insert hole 260B. Each planetary
rolling element 26B is supported by the planetary carrier pin 33B
to be capable of rotating and revolving. A planetary carrier 34B
including the planetary carrier pins 33B is fixed to the eccentric
shaft 21B, which will be described below. In addition, an outer
circumferential portion of each planetary rolling element 26B
includes a plurality of planetary teeth 261B arranged to mesh with
sun teeth 141B of the sun rotor 14B. Thus, the rotation of the sun
rotor 14B at the first rotation rate causes each planetary rolling
element 26B to revolve around the central axis 90B at a second
rotation rate lower than the first rotation rate in the same
direction as a direction in which the input shaft member 10B and
the sun rotor 14B rotate. Note that the planetary rolling elements
26B may alternatively be arranged at irregular intervals around the
sun rotor 14B.
The eccentric shaft 21B is a tubular member including an outer
circumferential surface which is eccentric with respect to the
central axis 90B. Due to the revolution of the planetary rolling
elements 26B around the central axis 90B, the eccentric shaft 21B
receives power through the planetary carrier 34B, and rotates about
the central axis 90B at the second rotation rate in the same
direction as the direction in which the input shaft member 10B and
the sun rotor 14B rotate.
In addition, a plurality of second bearings 25B are arranged
radially between an inner circumferential surface of the eccentric
shaft 21B and the input shaft member 10B. This contributes to
increasing precision with which each member of the speed reducer 1B
is arranged. This in turn contributes to stabilizing rotation of
the eccentric shaft 21B, and reducing wear and damage of each
member, and also contributes to extending the life of the speed
reducer 1B.
At least one of the plurality of second bearings 25B (a second
bearing 25B1 in FIG. 4) is preferably a ball bearing. In the case
where the "helical gear" is used as each of the planetary rolling
elements 26B as described above, an axial load occurs. In this
case, use of the ball bearing leads to easier absorption of the
axial load. In addition, at least one of the second bearings 25B (a
second bearing 25B2 in FIG. 4) is preferably a needle bearing. This
contributes to reducing the radial dimension of the speed reducer
1B.
The internal ring 36B is a member in the shape of a circular ring,
including a contact surface arranged to make contact with the
planetary rolling elements 26B, and arranged radially outward of
the planetary rolling elements 26B. The internal ring 36B is fixed
to the output flange 30B. In addition, the internal ring 36B
includes a plurality of internal teeth 361B arranged to mesh with
the planetary teeth 261B in an inner circumferential portion
thereof. Each of the planetary rolling elements 26B constantly
meshes with both the sun teeth 141B of the sun rotor 14B and the
internal teeth 361B of the internal ring 36B.
The first eccentric oscillating gear 22B is attached to an
eccentric outer circumferential surface 211B of the eccentric shaft
21B through a first bearing 24B. Therefore, the first eccentric
oscillating gear 22B is supported to be rotatable about a first
central axis 91B, which is a center of the eccentric outer
circumferential surface 211B of the eccentric shaft 21B. Similarly,
the second eccentric oscillating gear 82B is attached to an
eccentric outer circumferential surface 811B of the eccentric shaft
21B through a first bearing 84B. Therefore, the second eccentric
oscillating gear 82B is supported to be rotatable about a second
central axis 92B, which is a center of the eccentric outer
circumferential surface 811B of the eccentric shaft 21B.
The output flange 30B includes the first disk 31B, a second disk
32B, and a plurality of eccentric oscillating carrier pins 44B
arranged to pass through the eccentric oscillating gears (i.e., the
first and second eccentric oscillating gears 22B and 82B) in the
axial direction. Accordingly, rotation of the eccentric oscillating
gears (i.e., the first and second eccentric oscillating gears 22B
and 82B) causes power to be transferred to the output flange 30B
through the eccentric oscillating carrier pins 44B.
Further, third bearings 60B are arranged radially between the
eccentric shaft 21B and the first and second disks 31B and 32B of
the output flange 30B. This contributes to further increasing the
precision with which the output flange 30B is arranged in the speed
reducer 1B. This in turn contributes to stabilizing rotation of the
output flange 30B, and further reducing the wear and damage of each
member, and also contributes to further extending the life of the
speed reducer 1B, as is similarly the case with the first preferred
embodiment.
As illustrated in FIG. 4, at least one of the third bearings 60B is
preferably arranged to axially overlap with at least one of the
second bearings 25B. This makes it easier to align centers of
rotation thereof with each other. Moreover, a reduction in the
thickness of the eccentric shaft 21B can thus be achieved, which
contributes to reducing the radial dimension of the speed reducer
1B.
As described above, in the present preferred embodiment, the
internal ring 36B and the output flange 30B, which are fixed to
each other, receive power through the planetary rolling elements
26B and the eccentric oscillating carrier pins 44B. Accordingly,
the internal ring 36B and the output flange 30B revolve around the
central axis 90B at a third rotation rate lower than the second
rotation rate in a direction opposite to the direction in which the
input shaft member 10B and the sun rotor 14B rotate.
While preferred embodiments of the present invention have been
described above, it will be understood that the present invention
is not limited to the above-described preferred embodiments.
Note that the detailed shape of each speed reducer may be different
from the shape thereof as illustrated in the accompanying drawings
of the present application.
Preferred embodiments of the present invention are applicable to
speed reducers.
Features of the above-described preferred embodiments and the
modifications thereof may be combined appropriately as long as no
conflict arises.
While preferred embodiments of the present invention have been
described above, it is to be understood that variations and
modifications will be apparent to those skilled in the art without
departing from the scope and spirit of the present invention. The
scope of the present invention, therefore, is to be determined
solely by the following claims.
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